Fluid driven motor pump



May 2, 1939. J. D. MATHEWS FLUID DRIVEN MOTOR PUMP e Sheets-Sheet 1 Filed Aug. 15, 1935 M m m v4 nm/ a i J M v .5 w wu a w @020. am 5 WW6 May 2, 1939- .1. D. MATHEWS FLUID DRIVEN MOTOR PUMP 6 Sheds-Sheet 2 Filed Aug. 15, 1935 mar/I, 6 l

INVENTOR ATTORNEY May 2, 1939. J. D. MATHEWS FLUID DRIVEN MOTOR PUMP Filed Aug. 15, 1935 6 Sheets-Sheet 3 INVENTCR I ATTORNE'Y May 2, 1 939 J. D.MATHEWS FLUID DRIVEN Mo'i'oR PUMP Filed Aug. 1'5, 1935 arr- 6 Sheets-Sheet 4 INVENTOR ATTORNEY y 2, 1 J. p. MATHEWS 2,156,537

FLUID DRIVEN MO;1OR BUMP Filed Aug. 1S, 1935 I 6 Sheet-Sheet s Patented May 2, 1939 UNIT D- STATES FLUID DRIVEN MoronrPUMr John D. Mathews, Oklahoma City, Okla.- Application August 1 5, 1935, Serial No. 36,383 v 26 Claims. (01; 103-46) i I My invention relates to fluid driven motor pumps, and more particularly to such pumps for use in lifting liquids from bored wells.

At the present time motor-pumps for this purpose require a power unit upon the earth's surface for delivering a fluid under pressure through a tube or pipe line to the motor situated within the well.

The usual motor comprises substantially: a piston head and rod 'reciprocatably mounted within a barrel and having upper and lower faces which oppose respectively an upper and lower cylinder head within the barrel; valve means' for delivering the power fluid to within the barrel alternately above and below the piston head; valve means for exhausting used power' fluid alternately from within the barrel below and above the piston head in timed relation to the delivery. of the power fluid; and a motor exhaust conduit into a production tubing or above a packer into the casing. The usual pump associated with and actuated by the motor comprises: a working barrel, a piston reciprocatably mounted therein and connected to the motor piston head by a piston rod; suitable valved intake and discharge ports for production fluid; and, a pump discharge conduit leading into production tubing or into the well casing above a packer.

Insofar as I have been able to learn there has never been applied in fluid driven motor pumps a principle permitting total motor piston' area of more than a fraction of the total cross sectional area of the casing bore. This limit has necessitated the use of excessively high pressures for actuating even very small pumps.

Other obstacles to be met vary between the motor pumps driven by a gaseous fluid and those driven by a liquid. v I

-In motor-pumps using a liquid as a power fluid great difliculty has been encountered in valving the long moving columns of the liquid. When the columns are valved in a usual manner, such great pressures are developed by stoppage of the moving columns at each stroke that, in order to prevent bursting, the motor-pump must be operated at low velocities in comparison with usual pumppractice, thereby limiting sharply the quantity which can be pumped, more particularly from deep wells.

a gaseous power fluid, even though the readily compressible nature of such fluid together with the high pressures. under which it must be placed require extremely large volume and'consequently expensive power generating equipment at the earth's surface, which entails high operating cost.

My motor-pump eliminates the difficulties 5 enumerated in both types of fluid driven motorpumps, accomplishes quantity production, and operates, upon a power fluid delivered at an optional pressure approximating one'halfto even jvalving principle and mechanism; which em- 20 bodies a new and novel method "of power fluid delivery and exhaust disposal particularly suited to simplicity in the application of my principle of selective piston ratio amplification; which is capable of operation under all known well condi- 25 tions, in either deep or shallow wells; which'may be positioned and sealed in a well without use of a packer; which is capable of installation in wells in such a manner as to provide means for excess gas pressure disposal and for maintenance of 30 desirable gas pressure in the well when such pressure is present; and, which includes means for preventing the entry of foreign substances into the working mechanism;

Other objects of the invention are to provide 35 a device of this class which is new, novel, practical and of utility; which may be lowered into a well upon production tubing surrounding a fluid power delivery tube, so that thereafter, the delivery tube may be removed from the well to per- 40 mit cleaning of the production tubing without affecting the device; which, upon receiving a supply of power fluid, will start from any point in the cycle of the motor; which includes a fluid means for stopping and preventing injury to the 45 fvalve at each endof its stroke; which may have a constant useful motor piston area in each end" of the piston chamber; which maybe operated at high speed even in extremely deep wells; and, which will be eflicient in accomplishing all the 50 purposes for which it is intended.

Heretofore, in fluid driven unitary motorpumps in wells, the working area of the motor piston has been restricted to considerably less than the cross sectional area of the well casing,

of motive fluid in the above ground pump or compressor, in the power fluid conveying line, and in the motor-pump atthe bottom of the well, particularly in deep wells, thus limiting sharply the amount of liquid possible to be delivered by the pump. The limit which the present dimension of the well casing places upon the size of themotor piston, together with the highest practical pressure at which the power fluid can be delivered,

' combine to set .an absolute limit upon the depth at which a pump of given capacity canbe operated practically.

My invention provides an eflicient fluid driven motor-pump which produces novel results through use of a new principle for the selective amplification of the working area of the motor piston far beyond the limit set by the size of the well casing. I

My method generally, includes the use of a combination of a vertical series of .co-acting -motor piston faces and chambers, with means for supply, control, and exhaust of power fluid.

Specifically, for a given pump piston area with power fluid delivered to the motor at the highest practical pressure, by multiplying the motor piston area, Lmultiply the force which can be exerted on a pump of given size, therefore multiplying the depth at which the motor-pump will 30 operate. i

In comparison with present fluid driven motorpumps operating at the same depth, by'doubling or tripling the useful motor piston area, my motor-pump can operate upon the same power fluid pressure, and the size of the pump piston can be dou' ed r tripled, thus doubling or tripling the J volume of well 'fluid delivered to the earth's surface. Or, in operating a pump piston of a size and at a depth the same as those of present fluid driven motor-pumps, I can, by doubling or tripling the working area of the motor piston, operate my motor-pump upon one-half or one-third of the power fluid pressure ordinarily required, thus permitting the elimination of all high pressure equipment and gaining a new and more:

desirable mode of operation.

In present fluid driven motor-pumps, so far as I have been able to ascertain, there has not heretofore been' provided a valving means which does not stop the flow of power fluid to one end of the motor piston chamber before admitting it to the opposite-end of the chamber, thus stopping completely, though momentarily, all flow of power In an analogous manner all flow of exhaust motor fluid from the chamber is stopped completely at the instant of valve shift at the end of .each stroke.

The result of the complete stoppage of the flow into the motor, when a liquid is used as the power fluid, is the stoppage of the entire columnof virtually incompressible liquid, and the conversion of the momentum-of the column into. a

.rapidly built up excessive pressure which centers at the point of valving, producing an extreme shock, or what is commonly known as water.

hammer. Heretofore, insofar as I have been able to ascertain, there has been no method developed of either preventing water hammer in liquid driven motor-pumps, or of absorbing the shock, therefore prohibiting the operation of liquid driven-motorpumpsat any but low velocf ities in order to prevent bursting. In my invention this problem is solved in valving by the use of a novel relation of ports, cloconsequently entailing excessively high pressures sures, and timing which allows uninterrupted flow of power fluid into and exhaust fluid out of the motor, thereby eliminating the cause of water hammer. My novel relationof. ports, closures and timing is identical whether that relationship exists in one compound or in several separate valve structures of any type.' In my preferred embodiment the valve closure of the one valve begins to register and diminish the flow of power fluid into the one end of the motor piston chamber, and simultaneously the port of the other intake valve begins to register and permit the flow of the power fluid to the opposite end of the motor piston chamber in direct proportion.

The valve shift begins, proceeds, and is completed without changing either the combined intake port area or' the combined exhaust port area.

I Obviously an action lessdesirable, due to excessive loss of power fluid and excessive time required for the shift, could be obtained by opening the second port completely before the first port begins to close, instead of having the opening and closing occur simultaneously. Such action would be based upon the principle used in my preferred embodiment, of not closing the one intakeport before opening the second.

In the preferred embodiment of my invention, the entire pumping mechanism is located above and intakes from above the motor, thereby eliminating the conduit otherwise within the assembly for conducting the production fluid past the motor. Various benefits are derived from such an arrangement, some of which are: greater motor piston area; increase of pump intake area;

reduction of interference with pump valves by' the motor piston may be identical upon both the upward and downward strokes. This produces a uniformly smoothpiston .travel and therefore permits a much higher piston speed than is usually possible.

With these and other objects in view aswill more fully appear hereinbelow, my invention consists in the construction, novel features, and combination of parts hereinafter more fully described, pointed out in the claims hereto appended,and illustrated in the accompanying drawings, in which,

Figure 1' is a vertical section of the upper portion of my motor-pump, and shows particularly the construction of a preferred type head, as well as that portion of the device which is positioned immediately therebelow Figure 2.is a transverse section taken along the line 2-2 of Figure 1;

Figure 3 is a transverse section taken along the line 3'3.of Figure 1;

Figure 4 is a fragmentai vertical sectional view of the portion of the device lying below Fig. 3;

' Figure 5 is a sectional view taken along the line 55 of Fig. 4;-

Fig. 6 is aview similar to Fig.4 but is taken at-a radial position-ninety degrees to the right hand of that at which Fig. (was takeny.

Figure 7 is a p along the line 1-1 of Fig. 6;

Figure 8 is a fragmentary detail of. a portion of the device;

Figure 9 is a fragmentary vertical sectional transverse sectional view taken view of the portion of the device lying Figs. 4 and 6;

Figures 10 andll are respectively transversethe portion of the device that lies directly below the portion shown in Fig. 9; I

Figures 13, 14, and 15 are transverse sections taken respectively along the lines |3-|3, |4|4 and I5-|5 of Fig. 12;

' Figure 16 is a fragmentary vertical sectional view of the portion of the device lying directly below the portion shown inFig. 12;

Figure 17 is a fragmentary view of the. portion of the device lying directly below the portion shown inFig. 16 and is partially in section;

Fig. 18 is a schematic view of my complete pumping device including a head (Fig. 1) and the pump and motor structure, embodying two motor units. The pistons are at the bottom of their stroke;

Fig. 19 is a view identical to Fig. 18 except that the pistons are at the upper end of their stroke, and the valve parts in corresponding position.

Like characters of reference designate like parts in all the figures.

It is understood that various changes in the form, proportion, size, shape, weight and other details of construction, within the scope of my invention may be resorted to without departing from the spirit or broad principle of my invention and without-sacrificing any of the advantages thereof and it is also understood that the drawings are to be interpreted as being illustrative and not restrictive.

The inventive idea involved is capable of receiving.a variety of mechanical expressions one of which, for the purpose of illustrating the invention, is shown in the accompanying drawings.

I now refer more particularly to Figs. 1, 2, and 3 of the drawings in which is illustrated a head particularly adaptable for use in an extremely sandy condition of the production fluid, the power fluid, and/or if the well is without liner.

The reference numeral 3 indicates the lower end of a tubing string for delivering power fluid from the earth's surface. To this tubing string is attached the upper end of a hollow substantially cylindrical upper member 40 having a hemispherically concave ground joint seat 4| in its lower end, and a central lower reduced orifice 42.

A lower'hollow member 43 having a longitudinal bore 44 and an upper hemispherically convex ground joint seat to fit within the seat 4| is provided beneath the member 48 and is held in position by a coupling 45 and the upper end of a pipe 13. If preferred the member 43 may be made integral with the coupling 45, but if not the two should be arranged in assembled relation before the following described passages are formed therein.

It will be noted that the convex upper end of the member 43 will properly seat within the seat 4| even though the tubing string 3 is disposed at an angle with relation to the member 43. The coupling 45 is equipped with a plurality of radially spaced passages 4'1, and also with another set of drain passages 48. The passages 41 are radially alternated with the passages 48, and lead below 7 joined to the coupling 45. The tubing 49 extends to the earth's surface. The-passages 48 extend downwardly from the convex seating sur-' face of the member 43 and outwardly through the side walls of the member and through the wall of the coupling 45.

Positioned within the bore 44 of the member 43 is an upwardly closing check valve structure in the annular space around the tubing 15,

through the passages 41 and into the tubing string 49.

Proceeding with the description of the motorpump proper, the tubing 15 is provided with a longitudinally'extending partition 18, which begins at a point near the upper end of the tubing 15, as shown in Fig. 1, and extends to the opposite end of the tubing, as illustrated diagrammaticaily in Fig. 18. The partition 18 at its up per end converges with and is connected to one outer wall of the tubing 15, and below this point forms two separate longitudinally extending passages l9 and 80. The passage 19 communicates with the tubing 3 to convey power fluid downwardly, while the passage 88 is for conveying used power fluid upwardly. A lateral port 8| forms a communication between the passage 88 and the passages 41.

A cylindrical plunger sleeve 82 loosely surrounds the tubing 15 forming an annular passage for discharge of produced fluid, and at its lower end the sleeve 82 is threaded into the up per end of. a slidable pump piston head 83. A second cylindrical sleeve or liner 84 is pressed into the barrel "l3 and positioned around the sleeve 82, as shown in Fig. l. The two sleeves 82 and 84 are ground-to a liquid tight fit with each other.

An enlarged section 85 of the pump barrel is threadedly connected to the lower end of the section 13, andhas a plurality of breathing ports 86. The sleeve84 terminates just above the ports 86. A sleeve 8| is pressed rigidly in position around the pump piston head member 83, and becomes apart thereof. Around the tube 15 and within'the sleeve 82 and piston head 83, is left an annular space 88 which communicates at its upper end within the section 13 and with the passages 41. p

Attached to the lower end of the piston head 83 by threads 89 (Fig. 4), is a lower head section 90 having a plurality of upwardly extending ra.--

dially spaced ports 9|, each of which is provided with a ball check 92. The ports 9| at their lower ends diverge outwardly through the wall of the lower head section 98. An annular space 93 is provided between the outer surface of the head section 90 and the inner surface of the barrel section 85. The ports 9| form a means of communication between the annular spaces 88 and 93 when the balls 92 are unseated.

As best may be seen in Figs. 4, 5, 6-and 7, the tube 15 is provided .in its walls with a pair of oppositely disposed longitudinally extending grooves 94 and 95, and as shown in Figs. 6, 7 and 8,'the head section 90 is equipped with two run-1 ners 96 which are anchored with the head section 90 andwhich slide within the grooves 94 and 95. The runners 96 are. held within the head section 90 by the upper end of a hollow piston rod 91 which is threaded into the head section 90, and which impinges a laterally extending lug 99 (Figs. 6 and 8) upon each of the runners. The grooves 94 and 95 and the runners 96 co-act with a member I63 (Fig. 16) to preventany rotative action of the motor piston head therebelow with relation to the tube 15. l

The lower end of the barrel section 85 is con nected by a coupling 99 (Fig. 9) to the upper end of a tubular packing-gland housing and intake port sleeve I00. The coupling 99 also acts as a check valve and packing housing.

' The lower portion of the coupling 99 is internally threaded and receives in turn, starting at the upper ends of ts threads, two metal rings IOI and I02, the annular flange I09. of a cupleather I04, a cushion ring I05 of leather, a jambnut I06 for holding the flange and cushion ring firmly against the ring I02, an annular cage I01 for retaining check valve balls I08, and a lower annular ball cage I09 for retaining the balls. The elements IOI, I02, I03, I05, I06, I01, and I09 are all provided with radially spaced through perforations adapted to be aligned to form a plurality-f the rough passages, and the lower cage member I09 has seats for the balls at the upper orifice of each of its perforations. the upper cage member I01 is spaced sufficiently from these seats-to permit the balls to become unseated for allowing upward flow of a fluid. The members IOI, I02, I03, I04, I05, I06, I01, and I09 are all formed in segmental sections in order to, permit their assembly about piston rod- 91. The ends of the various segments are illustrated by radial lines in Fig. 11.

At a point beneath the lower cage member I09, the sleeve I00.is provided with a plurality of radially spaced intake slots or ports IIO for receiving production fluid from the well.

-Below the-ports IIO the sleeve I00 is internally threaded as shown at III and H2. The larger threads II2 are for coupling the sleeve to a tubular power unit housing I I3, (Fig. 12) and the smaller threads III receive the following packing movement will seat all of the balls 92. This will elements in turn starting at their upper end:-

A metal seatingring II4; a resilient packing ring II5; a lamb-nut I20; aleather cushioning 'r'ing I2I;- the-flange IIG of ajcup-leather I";

an annular jamb-nut H8; and, an annular. locknut H9. The members H4, H5, H6, H1, H9, H9, I20 and I2I are all formed in segmental sections in order to permit their assembly around the rod 91.

'The operation of the pump above described may be explained as follows:

It should first be taken for granted that a power is to be furnished (motor will be later described) for imparting a reciprocal motion to the tubular piston rod 91,

The first upward movement of the rod 91will move. the pump piston head. members 90 and 83 (Figs. 4 and'l) .and the sleeve 82 .upward, which remove downward pressure upon the balls I00 (Fig. 9) thereby permitting them to be lifted by the static head pressure of the outside fluid, and permitting the flow of the outside fluid through the ports III and into the annular space 93 being vacated by the piston members 90 and 91. Downward movement of the rod 91 and the piston head member 99 and 03 will seat the balls I99 and unseat the balls 92.to'permit the production fluid The wall of 1 chamber is discharged the remaining one-half' volume through the openings 41. The next upward stroke will not only 1111 the annular space 93 lying below the piston, but will seat theballs 92 and force the fluid above plunger sleeve 92 upward through the annular space 99, through the openings 41', and into the annular space between the tubes 9 and 49, from whence on the following strokes of the piston It will be forced from the upper end of this space at the earth's surface.

each stroke. providing balanced action and balanced load. i A,

The ports 86 (Fig. 1) areprovided in order to permit adjacent interior annular space: to be Thus it will be noted that the pump discharges from chamber 89' an equal volume on i filled with the well fluid upon the downstrokeand to be emptied upon the upstroke. This-gives what might well be termed a breather effect.

It will be noted that neither the balls nor I08 aredivided'by any cage, which'is conventional with ball check valves ingeneral, but instead depend upon the annular space within which they are contained, and upon each other for proper alinement o'ver theirrespective passages. (See Fig. 5.) *2

Each of the balls 92 is seated in the upper end of one of the ports 9| and when in a seated positionapproximatelyjone-half of its diameter lies within the port. The lower end of the member 93 lies sufficiently close'tofthe upper surfaces of the balls to prevent the -,escape of each ball from a vertical position. over its respective port 9|. The ports 9I are sufficiently close together to insure proper seating of one of-the balls over I each p'ort,even though the lower end of the member ,93 was positioned a greater distance from the balls, provided of course that the distance is-not greater thantwice the diameter of reference to Figs, 12 to 19 inclusive.

The piston chamber housing II3 which has a smooth interior surface is threadedly engaged at its upper end into the threads I I2. of element I00. The tubular piston rod 91, at a point in the upper portion of the housing H3, is enlarged exteriorly but not interiorly, and while shown to be of one piece construction, it is obvious a similar result may be obtained by use-of a threaded cuff, and this enlarged portion I30 is provided with exterior threads I3I. The bore of the element 91 is slightly enlarged at its extreme lower end as indicated by the reference numeral I32. The threads I3I engage the upper end of a substantially tubular outer piston shell I99, which centrally is provided with an annular inward pro tion with notch I35 are a plurality of radially spaced vertical passages I31, which extend upwardly in the wall of the shell I33 to its extreme upper end. Extending downwardly within the wall of the shell I33 from the groove I36 to its lower end is a plurality of radially spaced passages I38 similar to the passages I31 thereabove.

and. 95 in the tube 15 to prevent its independent rotation with relation to the sleeve I 39. Around the sleeve I39 but less in length is a sildable sleeve valve I*4I. The sleeve I39 is held rigidly in place and the downward movement of the sliding valve MI is limited by the upper end of an. externally threaded substantially tubular head I42, which is threaded into the lower end of the shell I33, and which head forms the lower end of the power piston which drives the tubular pis Y ton rod 91 to reciprocation. The lower end of the power piston is indicated by the numeral I45. The annular space between shell I33 and the sleeve I39 within which the sliding valve MI is permitted a limited reciprocal movement is in- I dicated by the reference numerals I44 (Fig. 12);

The sliding valve MI is provided on its inner surface with two longitudinal extruded splines, or tongues, I43 which have asliding engagement within the indentations I40 of-the port carrying sleeve I39.

l The tube 15 has two oppositely disposed longitudinal through slots I46 and I41 which respectively communicate with the passages 19 and 80 at opposite sides of the partition 18. The respective upper ends of the slots I46 and I 41 are indicated by reference numerals I48 andi49 (Fig. 12) and their respective lower ends are indicated by numerals I 50 and I5I (Fig. 16). The length of the slots I46 and I41 are approximately equal to the length of stroke of the power piston, plus the distance between the bottom of the port I54 and the top of the port I52, plus the overthrow distance at each end. I v

The port carrying sleeve I39 has two upper lateral through ports I52 and I53 (Fig. 12). which are oppositely disposed and which arevradially coincidental respectively, with the slots I46 and l41nin the tube 15, and is alsoprovided with two lower through ports I54 and I55 which are radially spaced similarly and in respective vertical alignment with the ports I52 and 153." The two upper ports I52 and I53 are vertically' coincidental with the groove I35 in'the shell I33 while the lower ports I54 and I55 are vertically coincidental with the groove I36 in the shell I33. J r

In order to illustrate the relative lengths of theannular space I44, with the. valve sleeve MI, and the lengths and spacing of the ports I52 and I54, and I53'and I55, with relation to the length,

of the space I44 and the length of the sleeve I4I,

will be more fully described hereinbelow, only.

twelve parts of the space I44 are utilized to acfourth part at each end of the space being used as afluid stop chamber.

The sliding valve MI is provided with a through port I56 the vertical center oi which lies an equal distance from each end of the sleeve. MI, and which is radially coincidental with the ports I52 and I54 in the sleeve I39. Said port I56 is three aliquot parts long with relation to the sleeve I, and its center is coincidental vertically with the center of. the port I54 when the valve is at the lower end of its throw, and with the center of the port I52 when the valve is at the upper end of its throw. The valve I4I also has two vertically spaced ports I51 and I58 each two parts in length, spaced apart vertically three parts, and which are radially coincidental with the ports I53 and I55 in the port carrying sleeve I39. The uppermost of these ports, I51, has its upper edge vertically alined with the upper edge of the .port I53 when the sliding valve is at the lowermost end of its throw, while the lower port, I58, has its lower edge alined vertically with the lower edge of the port I55 in the sleeve I39 when the valve is' at the upper end of its throw;

From the foregoing description it maybe seen that if a; power were to be generated to reciprocate' the sliding valve "I in proper timed intervals, and that if a fluid under suiiicient pressure was being delivered downwardly in the power commodate the valve sleeve MI in its travel, oneside of the tube 15, or in other words through the I9 of the tube 15 through the longitudinal slot I46 in the side of the tube 15, throughthe port I54 in the port carrying sleeve I39, through the port I 56 in the sliding valve I through the annular space or groove I36, and through the vertical passages I39 in the shell I33, into an annular space or piston chamber I59 below the power piston head. Considering the space I59 to be closed at its lower end, the piston head would therefore be moved in an upward direction, providing exhaust of any fluid in the piston chamber above the piston and below the packing gland in the lower end of the sleevev I60 is simultaneously permitted.

During this upward movement, a discharge is being. permitted from the piston chamber above the piston head downward through the passages I31 in the shell I33; through the groove I35,

through the port I 51 in the sliding valve I,

through the port I53 in the port carrying sleeve I39, thrcughthe longitudinal slot I41 in the tube 15,, aird into the-exhaust .space or passage 86 in the tube 15 where it is free to move upwardly to discharge through the head (Fig.1) above the previously described pumping unit, and into the.

production tubing 49.

If, when the power piston reaches the approximate upper end of its stroke, the sliding valve I M should be suddenly powered to move to the upper end of its throw, the power fluid would be permitted to flow from the passage 19 through the longitudinal slot I46 in the tube 15; through the port I52 in the port carrying sleeve I39, through the port I56 in the sliding valve I, through the annular space I35, and through the vertical passages I31 into the chamber above the power piston. This would alter the direction of movement of the piston and start it in a downward direction pr oviding fluid in the chamber I59 were permitted to exhaust.

Upward movement of the valve would simultaneously permit exhaust of the fluid from the chamber I59 below the power piston through the vertical passages I38 in the shell I33, through the annular groove I36, through the port I58 in the sliding valve I4I, through port I55 in the port carrying sleeve I 39, and through the longitudiiial slot I41 in the tube 15 into the exhaust passage 80; This cycle would of course be repeated as long as the power .fiuid was being de- 'livered.

The lower end of the head I42 (Fig. 12) is made integral with the upper end of a'section I60 of piston rod which is identical in cross section to the piston rod 91 above the power piston. The section I60 terminates below the chamber I59 in a threaded head I6I (Fig. 16). A ring I63 carrying two upwardly extending splines which are adapted to travel in the grooves 94 and-95 in the tube 15, is provided around the lower end. ofthe head I6I, and is held in place by a cap- I62 threaded on to the head I6I. The element I63 serves, together with the members 96 (Figs. 7 and 8) to lock the entire piston assembly against independent'rotation upon the tube 15.

The lower end of the barrel II3 (Fig. 16) is I connected by an interiorly threaded coupling I65 formed in segmental sections to permit assembly to a pipe section I66 which acts as a housing for the lowerfend of the tube 15, which tube extends slightly below the lower end of the piston rod I60, when that'rod is at the lower end of its .stroke. The grooves 94 and 95 extend entirely to-the lower end of the tube15, which is seated at its lower end in a socket in the upper sur-' face of a thrust nut I61 (Fig. 1'7) carried by a coupling I68, which-in turn is threadedly attached to the lower end of the pipe I66. The

coupling I69 also carries a'lock-nut I69 for pre venting inadvertent loosening of the thrust nut 1 I61. The lower end of the coupling I69 is pref- .erably closed by a pipe I10 which has a closed lower end.

'The'previously described coupling I65 (Fig. 16)

is interiorly threaded in its central portion and acts as the housing for a packing glandwhich preferably comprises the following superimposed elements beginning at the bottom of the threads:

a seating ring "I; a resilient packing ring I12;

a'jamb-nut I13; the flange I16 of a cup-leather I15; a. leather cushioning ring I14; a.jamb-nut- I11; and, a lock-nut. I18. The packing elements last .above described act to close the bottom of the piston chamber I59, and each is I at each end of each stroke of the power piston the following described structure is .em-' ployed. r

Adjacent the upper end of the port carrying sleeve I39 (Fig. 12), aslight distance below the upper end of the annular space I44 within which the slide valve I4I reciprocates, and radially at passage 19 of the tube.

approximately sixty-five degrees from the position of the slot I41 in the tube 15, the port carrying sleeve I39 is provided with a through perforation or port I the top edge of which is slightly below the upper end of the annular space 144 and which communicates therewith. In the same radial position, and in such a vertical position'as to cause its lower end to register with the port I80 when the power piston is approximately at the upper end of its throw, a longitudinally extending through slot or port I8I is provided in the wall of the tube 15. The port ,I8I opens into the exhaust passage 80 of the tube 15. At a radial position lying approximately fifty degrees to the left hand of the port I80, the port carrying sleeve I39 is provided with a port I82 the top edge of which is coincidental with the upper end of the annular space I44 and communicates therewith. This port I82 is in such radial position as to afford communication between the space I44 and the power delivery Adjacent its lower end, and lying approximately one hundred and eighty degrees from the port I80, the port carrying sleeve I39 is provided with a similar port I83 having its lower edgecoincidental with the lower end of the annular space I44 and communicating therewith. At aradial position lying approximately one hundred and eighty degrees from the slot or port I9I, and in such a vertical position as to cause its lower end to register with the port I83 when the power'piston is approximately at the'upper end of its stroke, the tube 15 is provided with a longitudinal slot or port I85. The port I 85 opens into the power delivery passage 19 of the tube 15..

As may best be seenin Fig. 16, the tube 15 is provided with two other longitudinal ports or slots, the upper one of which is designated by the reference numeral I86 and the lower one by thenumeral I81.

The port I86 is in the same radial position as is the port I82 in the port carrying sleeve I39, andis in such a vertical position as to cause the port I82 to register with its upper end when the power piston is at approximately the lower end of its'stroke.

The port I91 is in the same radial position as is the port I84 (Fig. 12) in the port carrying sleeve- I39, and is in such a vertical position as to cause the port I94 to register with its upper end when the power piston is at approximately the lower end of its stroke.

As is clearly shown, the-port I96 passesthrough the. wall of the tube 15 lying within'thepowerstroke, and the port I 83 has registered with the lower end of the port I85 so that power fluid may pass into the annular space I44 beneath the sliding valve ;I4I to cause it to shift'upwardly in its annular space. At the same time, the port I80 has just registered with the lower end of the port I8I, and power fluid which is in the annular space I44 above the valve MI is free to exhaust intothe passage in order to permit the valve In to shift.

If the power piston is traveling slowly when this position is reached, the sliding valve will be moved instantly upward and the power piston will simultaneously, or approximately so, change its direction. However, if the power piston is traveling at a high rate of speed, it may travel upward a slight distance further, or until the ports .,I83 and I88 have reached, or closely approached, the upper ends respectively of the slots or ports I85 and I8I in the tube I5. In other words, the traveling speed of the power piston will determine the exact point at which the sliding valve .will complete its shift. At the upper end of the stroke of the power piston, the ports I82 and I84 in'the ported tube I39, and the ports I88 and I81 in the tube I5, perform n function.

During the downward movement of the power piston the Sliding valve I will remain in the upper end of the annular space I44 until the ports I82 and I84 in the ported tube or sleeve I39 simultaneously reach the upper ends respectively of the slots or ports I88 and I8! in the tube I5.

At this point the sliding valve will be moved downwardly by power fluid entering the annular space above the valve through the ports I86 and I82, and the fluid then in the annular space I44 below the valve will be exhausted into the passage 88 through the'ports I84 and I87, as the valve changes its position.

It will be noted that the ports I88 and I84, which form communication with the exhaust passage 88 in the tube I5, are slightly nearer together vertically than are the ports I82 and I83 which lead from the power delivery passage "I9. This is for the purpose of trapping a slight amount of the exhaust fluid in the annular space I44 to act as a cushion or stop for the sliding valve I at each end of its stroke. This stop is obtained because the exhaust-ports I88 and I 84 are located respectively a short distance below and above the upper and lower ends of the space I44 within which the valve I 4! shifts. Therefore a small amount of the fluid in the space is prevented from exhausting upon each stroke of the valve, thereby forming a fluid stop for the valve at each end of its stroke for preventing injury to the valve, and also providing a passage for the entrance of actuating fluid at opposite ends of r the valve. It will be noted that the valve MI always shifts in the direction inwhich the power piston is traveling. Also, that during the stroke of the piston, the valve II is held stationary with relation to the piston by power liquid trapped in the annular space I44 with no mode of escape.

Because of the fact that much less fluid pressure is required to reciprocate the sleeve valve I4I than is required to reciprocate the power piston, the fluid pressure in the fluid delivery passage 18 would be more than adequate to shift the sleeve valve, and thus the valve MI is assured positive action at all times.

A valve having such an arrangement of ports and closures as that shown in Figs. 12, 13, 14, 15' and 16 will function substantially as follows:

When fluid under pressure is admitted from the passage I9 through the ports I85 and I83 into the annular space I44 below the valve sleeve I, the valve sleeve will be forced upwardly, providing exhaust of the. fluid is permitted from the space I44 above the valve sleeve. This exhaust is accomplished by the co-incidence of the ports I88 and I8I which permit the fluid to.exhaust into the passage 88 and thence into the production tubing 49 thereabove. When the valve sleeve I4l has moved upwardly one aliquot part, closure of ports I53 and I54 begins, and the opening of piston chamber occurs. Upon completion of the above described motion of the valve sleeve I4I, the direction of the motion of the piston is reversed to move downwardly. Upon the piston nearing the lower end of its down stroke, the port I82 (Fig. 12) and the port I86 (Fig. 16) become co-incident and co-act to supply motive fluid from the passage I9 to the annular space I44 above the valve sleeve I4 I to shift it downwardly; and, ports I84 and I81 which are co incident, co-' act to permit exhaust of fluid from the annular space I44 below the valve sleeve I4I into the passage 88, from whence it passes upwardly to the production tubing. The last described motion of the valve sleeve progresses through three ali-' quot parts, and accomplishes reversal of motion 20 of the piston and completes its cycle.

It will be noted that motion of the valve sleeve- I4I equals three aliquot parts and is in the direction of the'piston travel. The direction of travel might be reversed by reversal of the. arrangement of ports, but the valveaction is intended to occur in the shortest possible period of time, thereby permitting a high piston speed, and this purpose is best accomplished by moving the valve sleeve in the direction of the piston motion.

The most common or universal method of valv ing, insofar as I am informed, is that in which the motive intake valve to a given piston cham-, ber is closed before the exhaust valve to said chamber is opened, thus preventing what iscommonly known as slip. This involves complete arrest or stoppage of motion inthe serving column of motive fluid, in this case a virtually incompressible liquid, and if the column is of any considerable height, or if it is moving at any considerable velocity, its force is opposed by the valve or valves. Valving in that manner is, to say the least, impractical and has the effect of producing a blow delivered at the valving point and extending throughout the apparatus, which is commonly known as water hammer.

In my device, with the valve sleeve I4I at the position shown in Fig. 12, ports I54. and I56 serve to supply piston motive fluid from the passage 19 to the lower end of the piston chamber, and 59 V the ports I53 and I5! serve to exhaust used motive fluid into the passage 88 from the opposite end of the piston chamber. Theports I83 and. I85 serve to supply valve motive fluid from the passage I9 to the annular space I44 .below the valve sleeve MI, and the ports I88 and I8I serve to exhaust used fluid from the annular space I44 above the valve sleeve I4I into the passage 88 from whence. it may pass into the production tubing. The piston is shown in Fig. 12 at the 88 ,point in its upward stroke when the ports serving the valve sleeve motive fluid below the valve, and the ports serving to exhaust fluid from above the valve sleeve, are co-incident. When the valve sleeve I4 moves upwardly one aliquot part, closure of ports I53 and I54 begins. and opening of ports I52 and I55 simultaneously begins. The ports named as closing; continue to close in exact proportion that those ports namedas'openin g,

open. At the medial point of total motion, each (0 of the four ports named are at one-half normal area therefore one-half flow of piston motive fluid passes from the motive fluid passage I8 through ports I46, I52, and. I56 into the annular space I35, and through ports I5I, I53 and I41 78 multaneously begun and proportionately increased into the opposite end of the chamber, and the exhaust ports serving each end of the piston chamber have moved simultaneously to positions where an exact balance of intake piston motive fluid port area and exhaust port area are equal at each end of the piston chamber and the piston comes to rest at the end of its stroke. Further upward travel of the valve sleeve I4I increases the proportion of piston motive fluid diverted to the upper end of the piston chamber and the piston moves in the opposite direction, or downwardly. This is repeated inversely at the lower endof the piston travel, substituting port I86 for port I85, port I82 for port I83, port I8'I for port I8I, and port I84 for port I80, and the piston cycle is completed.

Clear understanding of the foregoing description will disclose that at the medial point of motion of the valve sleeve I, the downward motion of the motive fluid in the passage I8, and the upward motion of the exhaust fluid in the passage 80, are each separately continued to the earth's surface. The motive fluid may move downwardly in the passage 19, pass through the ports in the piston and return upwardly through the passage 80 and the production tubing to the earths surface without change of impedance other than the frictional load, by reason of the fact that there is no arrest or impedance in the motion of the flow of the motive fluid during the period of valve shift, or during reversal'in the piston travel, and therefore there can not be what is commonly known as water hammer.

Attention is called to what may seem to be obvious, viz., that the port I56 in the sleeve MI actually serves as two ports by serving each end of the piston barrel with piston motive fluid. It seems obvious then that a sleeve increased in length over that shown, may be used, also that arrangement and location of the other ports may be varied, or that a series of separate valve slides for closure of the ports or even an entirely separate set of-valves might be used equivalently for accomplishment of the purpose, which is, an uninterrupted flow of a liquid power fluid.

It seems desirable to direct attention to provisions which have been made for the prevention of stalling on dead center. The valve sleeve I4I being independently supplied with motive fluid, depends for its movement only upon.

the co-incidence of the'ports' serving it, and when the piston reaches a given-point in its ,upward travel, incidence between the motive fluid port I83 carried by the piston, and the motive fluid port I85 occurs, and connection of the motive fluid passage I9 is established, and incidence of the exhaust port I carried by the piston, and the exhaust port I8I, causes connection with the exhaust passage 80, (ports I8I and I are in the form of slots carried in the stationary member 15). Thus motive fluid from the passage 19 enters the annular space I44 below the sleeve I, through the ports I83 and I85, and due to Similarly, one-half 'the piston.

the form of the port continues to furnish motive fluid to move the sleeve during further motion of Upon the total permissible motion of the sleeve, reversal of the motive fluid from below to above the piston is accomplished and the piston motion is reversed from upward to downward. When thepiston nears the end of its downward stroke motive fluid port- I82 carried by the piston becomes incident to the motive fluid port I86 (Fig. 16) and exhaust port I84 carried by the piston becomes'incident with the exhaust port I81, causing connection with the passage 80 carried by the stationary element I5. Motive fluid from the passage 19 thenenters the annular space I44 above the sleeve I4I through ports I82 and I86 and the sleeve is forced downwardly through its permissible motion at which time the piston motive fluid is diverted from its flow into the upper end of the piston chamber to flow into the lower end of the piston chamber,

completing a cycle. It is therefore obvious that valve action is entirely independent of momentum or piston motion, once incidence of motive fluid valve ports-occurs, and that if motive fluid is under pressure valve shift will occur. The foregoing paragraph applies equally whether a liquid or a gas valve is used.

It may appear from the foregoing that an alternative system of valving is suggested, this is not intended. The purpose of the use of the two described methods is an attempt to suit one device to use in all phases of pumping usually encountered in any one oil well. In nearly all wells a change of equipment for recovery of oil becomes necessary during the productive life of a well. When pumping first becomes necessary the well will usually supply enough natural gas for use as motive fluid and usually a gas lift is used. Later, when gas pressure is substan- .tially exhausted it is usual to remove the gas lift and use a sucker rod reciprocating pump. Therefore, if the present device is suited for use during the entire pumping life of the well it would render unnecessary the present requirement and loss of time and production incident to changing. equipment.

Furthermore, the use of the liquid valve alone and during the period when gas might be used would involve waste of gas during the gas producing period.

It may be thought that a gas valve alone would be adequate, substituting air for gas when suflicient gas became unavailable but all oil wells produce some gas as long as oil is produced and if air should be used the mixture of the air and the higher oil fractions and gas would form explosive mixtures which would thereby render that mode of production unavailable.

It is evident therefore that in practiceit will be desirable to supply with the device two valve sleeves one in which the ports ,are spaced suited to the use of gas and the other having ports spaced making it suited to the use of liquid. As set out hereinabove all other parts of the device in eithercase remain identical,

For emphasis in my' foregoing specific description, I have avoided my principle for ampliflcation of motor piston area as applied to my preferred embodiment, For simplicity and clarity of description the motor has hereinbefore been described as having but one motor piston and one motor piston barrel H3; and said barrel has been described as being connected by a coupling I65 to a housing I66 for the lower end of the tube 15 and piston rod I60.

My preferred embodiment actually has two motorpistons, as shown in Figs. 18 and 19. and two motor piston barrels, the second of which is situated directly below the first, and connected to thefirst by a gland containing coupling identical with the coupling I65; 'and the heretofore described coupling I65 connects the housing I66 to the lower end of the second motor piston barrel. The tube I5 is built the necessary extra length to serve the second motor piston as it serves the first; tube I5 then terminates within the thrust nut I61 as shown in Figs. 16 and 17; the piston rod I60 is also built the necessary extra length and connects the second piston to the first; the piston rod I60 extends from the lower end of the second piston through the coupling I65and terminates within the housing I66 as shown in Figs. 16 and 17, as previously described; the coupling connecting the two motor barrels contains gland members identical tothose closing respective ends of barrel H3; and all description relating directly to the motor barrel I I3 and its contents, applies also to the second motor barrel audits contents, and as well-to any additional barrels and their contents.

The force the motor is capable of exerting is directly proportional to the degree of amplification of. motor pistonarea, and the degree of amplification desirable depends both .upon the size of the pump to be actuated, and the depth from which liquid is to be pumped. The specific device described doubles the motor piston area through use of my amplification principle. As

much additional motor piston area amplification will be employed as each'individual well condition requires or justifies, by building a unit having the required number of motor pistons and piston chambers suited to a specific height of lift and to the motive fluid line pressure desired, it not bei g Possible to change characteristics of a unit by addition or subtraction of pistons and barrels, due to the fixed length of the element I5.

In further consideration of the power piston valve structure; it is pointed out that the piston in itself acts as a sliding valve over the tube I5,

and that its movement governs or times the shifting of the sleeve valve I II. Also that the port carrying sleeve l39 could be formed as a continuation orintegral part of the hollow piston rod I60, in which event the piston rod would actually be a part of the valve structure,'or, in other words would act as a timing valve over the tube I5. Or, the piston in itself could be arranged to carry the ports now carried by the port carrying sleeve I39. Also, that the hollow piston rod could be used over either a single power delivery or single exhaust tube, and other mechanical arrangements made to take care of either the second. receptacle which does not close thepassage to the first receptacle beforeopening said passage to the second .receptacle. It is obvious that the details of the valve structure might be changed and yet use this novel principle particularlyadapted to theprevention of water hammer in liquid driven motor-pumps; also that the 1 valving mechanism above described with relation to the power unit may be used to control fmov'ement of a single power piston, or-may be used as a unitary valving means for a series of power pistons and chambers; also, that details of the valve structure might be changed and yet use the novel principle involved in the opening and closing of the power intake ports and of the power exhaust ports in such a manner as to avoid stoppage of flow of the power fluid and consequent water hammer.

Obviously, the pumping unit could be positioned below the power unit if desired, by connecting a pump rod with the lower end of the power piston rod and by connecting the pump discharge to the lower end of the motor exhaust line 8. Such a device would operate, but many of the advantages present in the preferred-emof the tube 15 are not limited to those above .mentioned as it also serves as amain assembly shaft, as a locking member for preventing inadvertent separation of the assembled parts, and also carries ports for all valves used in the motor, acts as a breather means for the contents of the chamber formed within the element I66, and acts as a guide for causing proper registration of ports.

' Attention is particularly directed to the fact that the element I5 must in all instances be designed and built for a unit composed of a specific number of motor pistons and piston chambers, as well as for each desired length'of piston stroke. This is due to the shape of the element of any particular number of motor pistons and chambers. However, the unit may be designed area for a given size in cross-section. The oilices 15. Additional power units cannot be added to or I removed from a unit designed to be composed to give the desired power at a given pressure by one ormore power pistons and chambers.

Obviously the invention is susceptible of embodiment in forms other than that which is illustrated in the accompanying drawings and described herein, and applicable for uses and purposesother than as detailed, and I therefore consider as my own all such modifications and adaptations and other uses of the form of the device herein described as fairly fall within the scope of my invention.

Having thus described my invention, what is claimed and desired. to be secured by Letters Patent, is:

1. ma fluid driven motor-pump for boredwells, the combination with a piston chamber having a cylinder head at each of its ends, and with a piston rod and piston reciprocatably mounted within the'chamber, of a stationary combination delivery tube for power fluid and exhaust tube for used power fluid, said piston rod slidably mounted upon the tube and held against rotation with relation thereto, ports in the tube,

[other ports in the piston, and a reciprocal valve carried by the piston and controlling flow of fluid from the. tube to the chamber and from the chamber to the tube, for causing reciprocation of the piston. fluid driven motor-pump for bored wells,- the combination with a piston chamber having a cylinder head at each of its ends, and

with. apiston reciprocatably mounted within the chamber, of a hollow piston rodconnectedto 4. In a fluid driven motor-pump,-the combination with a reciprocatable piston within a housing, of a hollow stationary tube passing through the piston, a longitudinally extending partition within the tube dividing it into a power fluid delivery passage and a used power fluid exhaust passage, a hollow piston rod carrying the piston and slidably mounted around the tube and held in a fixed radial position with relation thereto, means carried by the piston for controlling the flow of a power fluid from-the delivery passage to reciprocate. the piston, and means carried by the piston for controlling the flow of used power fluid to deliver it into the exhaust passage in timed relation'to the action of the piston.

5. In a fluid driven motor-pump, the combination with a reciprocatable piston. a housing" therefor forming a piston chamber, said chamber being closed at each end, of a hollow stationary tube passing through the piston, a longitudinally extending partition within the tube dividing it into a power fluid delivery passage and a used power fluid exhaust passage, a hollow piston rod carrying the pistonand slidably 49- ior simultaneously exhausting used power fluid from the other end of the chamber into the exhaust passage for causing the piston to move in one direction, and means for changing the flow of power fluid to the said other end of the chamber and simultaneously changing the flow of used power fluid to the exhaust passage from the opposite end of the chamber at each end of each stroke of the piston to alterthe piston's direction or travel. 6. In a fluid driven motor-pump, the combination with a reciprocatable piston, a housing therefor, and a closed ended compression chamber at each end of the permitted stroke of the piston, of a hollow stationary tube passing partition within the tube-dividing it into a power fluid delivery passage and a used power fluidexhaust passage, a hollow piston rod carryingthe piston and slidably mounted around the tube and held in flxed radial positionwith relation thereto, ports carried by the',tube within the piston at each side of the partition therein, a

and communicating-with the chambers, said valve controlling flow of fluidi'rom the power passage to the chambers and the flow of fluid from the. chambers to the exhaust e in a manner causing reciprocation oi the piston. u

"I. In a fluid driven. motor-pump, the combiwith a reciprocatable piston, a housing therefor forming a piston chamber, said chamtionary tube passing through the piston, a longitudinally extending partition within the tube dividing it into a power fluid delivery passage and a used power fluid exhaust passage, a hollow piston rod carrying the piston and slidably mounted around the tube and held in flxed radial position with relation thereto, portscarried by the tube within the piston at each side of the partition therein, a port carrying sleeve carried by the piston, a port carrying sleeve valve slidably supported within the piston for opening and closing the ports in the tube, other ports carried by the piston and communicating with the chambers, said valve controlling flow of fluid from the power passage to the chambers and the flow of fluid from thejchambers to the exhaust passage, and fluid pressure means for shifting the valve at eachstroke of the piston for causing the piston to reciprocate.

8. Organization as described in claim '7, in

which the last mentioned means includes: ports carried by the tube at each side of its partition adjacent the positions the piston assumes at the ends of its stroke; and other ports carried by the port carrying sleeve and adapted to register with the ports in the tube, said other ports communicating with the space within which the sleeve valve travels.

9. In a fluid driven motor-pump, the combination with a piston and piston chamber, and with a power fluid delivery line and a motor exhaust line, of valve means for permitt the flow of P power fluid' into the chamber at one end of the piston, before cutting ofl '..the flow'oi power fluid into the chamber at the opposite end of the piston, and for permitting the flow of exhaust fluid from the chamber at one end of'the piston, before cutting ofl flow of exhaust fluid from the chamber at the opposite end of the piston.

' 10. In a fluid driven motor-pump,'the combination with a reciprocatable pump-piston, a mo-,

tor-piston, a hollow piston rod connecting the two, a piston chamber for each piston, and a sleeve connected to the free end of the motorof said pump piston chamber, whereby the pres sures within the pump-piston chamber, the tube,-

ing the reciprocation of the pistons and the sleeve.

11. In a fluid driven motor-pump for bored wells, the combination with a piston and a piston chamber, of a stationary delivery tube for delivering piston motive fluid to the chamber, and a stationary exhaust tube forexhausting used piston motive fluid iromthe chamber, bothof said tubes extending within the chamber from one end thereof to apoint lying beyond the most remote end of the permitted stroke of the piston.

' 12, In 'a fluid driven motor for deep wells. the combination with a plurality oi motor piston heads, and chambers in which they operate, of a piston rod connecting said head's, said piston and the closed ended chamber are equalized dur- 7 ber being closed at end. ot a hollow sta- I rod aflording' passageiorpiston motive fluid, 1

and fluid pressure actuated means for simulta neously delivering a fluid from the rod to similar .ends of each of the heads.

13. In a fluid driven motor pump the combination with a pump piston and chamber, of a plural number of motor piston chambers; a motor piston slidably mounted in each chamber; a piston rod connecting the motor pistons and the pump pistons; a means passing through each piston chamber and conveying the supply of motive fluid to said motor piston chambers, and a means passing through each piston chamber for conveying exhaust motive fluid from said motor piston chambers.

14. In a fluid driven motor-pump, the combination with a motor piston-chamber, a motorpiston reciprocatably mounted within the chamber, a motive fluid line, a motive fluid exhaust line, both lines having .ports for communicatingwith the chamber, and with a piston-rod connected to said motor-piston, of a pump piston chamber, a pump-piston within said chamber and connected to said pistonrod, said pump piston-chamber situated above said motor pistonchamber, said fluid conveying lines passing through said pump piston chamber.

15. In a fluid driven motor pump the combination with a pump piston and chamber, of a.'

fluid'driven motor including a plural number of motor piston chambers; a piston slidably mounted in each chamber, a control valve for controlling power fluid to and from each piston; a piston rod connecting the motor pistons and the pump piston; and a means passing througheach piston chamber for conveying a fluid for actuat-' ing the control valve.

16. In a fluid driven motor-pump, the combination with a motor piston, and a chamber with-' in which it reciprocates, of a ported valve carried by the piston, ports also carried by the piston, and stationary means within the piston rod for conveying a fluid to the ports for causinga timed shifting of the valve for controlling a piston motive fluid. 1

1'7. In a fluid driven motor pump, the combination with a motor piston, a motor piston chamber, and with a power fluid deliveryline, of valve means carried by said piston for controlling the flow of motive fluid to opposite sides of said piston within the chamber, and adapted to direct the flow of power fluid into the chamber at one end of the piston before cutting oil the flow of power fluid into the chamber at the opposite end of the piston.

18. In a fluid driven motor-pump for bored wells, the combination with a piston head reciprocatably mounted within a piston chamber,

of a hollow piston rod connected to the piston wells, the combination with a piston chamber having a cylinder head at each of its ends, and a piston .reciprocatably mounted within the chamber, of: a hollow piston rod connected to the piston; astationary delivery tube for piston motive fluid within the piston rod, said tube having ports for communicating with the chamber;

a valve for controlling the flow of motive fluid from the tube, and including the piston which slides along the tube and acts as a timing mechanism to control the shifting of the control valve.

said tube having, ports for communicatingwith the chamber; and a valve for controlling the flow of exhaust fluid into the tube, and, including the piston which slides along the tube andacts as a timing mechanism to control the shifting of the control valve.

' 21. In a fluid driven motor pump for deep 'wells, the combination with a piston chamber having a cylinder head at each of its ends, and

a piston reciprocatably mounted within the chamber, of: a hollow piston rod connected to the piston; a stationary delivery tube for piston motive and exhaust piston motive fluid within the piston rod, said rod and tubes having ports for communication with said chamber; and a valve for controlling flow of the fluid into and out ofthe tubes, and including the piston which slides along the tube and acts as a timing mechanism to control the shifting ofthe control valve.

22. In a fluid driven-motor pump for' deep wells, the combination with a piston chamber having a cylinder head at each of its ends, and a piston reciprocatably mounted within the chamber, of: a hollow piston rod connected to the piston; and a stationary delivery tube for piston motive and exhaust piston motive fluid within the piston rod, saidtubes being provided 1 with'ports aflording communication between the tubes and the chamber, said ports being of a length substantially equal to the length ofthe piston stroke.

23. In a fluiddriven motor pump for deep wells, the combination with a'hollow tube connected to a source of fluid pressure. and extending from the earth's surface into the well for der livering motive fluid to said motor pump, of a stationary longitudinally partitioned hollow tube having one of its longitudinal passages in communication with said delivery tube; a cylinder from the delivery tube into the opposite ends of the cylinder in timed relation to the piston movement, and for controlling the exhaust of used piston motive fluid from the opposite ends of the cylinder through properly spaced ports into the other of the passages of said partitioned tube v in timed relation to the piston movement.

- 24. In a fluid driven motor pump, the combination with a pump including a cylinder, a pump piston reciprocable in the cylinder, an inlet and an outlet for the cylinder, and a string of production tubing in communication with the outlet, of: a motor cylinder; a motor piston re-- ciprocable therein by'fluid pressure alternately supplied to oppositeends of the cylinder; a hollow piston rod extending from the pump cylinder into the motor cylinder and connected to both the pump and motor pistons; a stationary longitudinally 1 partitioned tube within the piston rod having a motive fluid delivery passage in communication with a remote source of fluid pressure supply and with the interior of the motor cylinder, and having a motive fluid exhaust passage in communication with said motor cylinder and said production tubing; and valve means for simultaneously and equi-proportionately-cutting 5 on the flow .of exhaust piston motive fluid from and permitting the flow of motive fluid into one end of the motor cylinder, and for simultaneously and equi-proportionately cutting on: the flow of piston motive fluid into and permitting the w flow of exhaust piston motive fluid out of the opposite end of the 'motor cylinder.

\ 25. In a fluid driven motor-pump, the combination with a piston chamber closed at each of its ends, a piston reciprocatably. mounted in the 15 chamber, and with-a piston motive fluid delivery line and a used piston motive fluid exhaust line,

of: intake and exhaust valve means associated with said delivery and exhaust lines for simultaneously, and equi-proportionately, cutting off the :9 flow of exhaust piston motive fluid from and affording flow of piston motive fluid into the chamher at one end of the piston, and for simultae neously, and equi-proportionately, cutting ofl the flow of piston motive fluid to and affording flow 25 of exhaust piston motive fluid from the chamber at the opposite end of the piston, said valve means adapted to provide constant flow of the motive fluid from the. delivery line into the piston chamber, and constant flow of exhausting 3o fluid from the piston chamber into said exhaust line, regardless of the direction of piston travel and regardless of the location of the piston in the chamber, thus eliminating the cause of fluid shock or water hammer, i. e. the complete though tainstantaneous stoppage oi the fast moving mofor, with a single hollow piston rod connecting both pistons together, with a central stationary hollow tube slidably fitted within said piston rod and on which said pistons and piston rod are adapted to reciprocate, said tube having two sep- 5 arate longitudinal passages therein, one for power fluid delivery and one for used power fluid exhaust, and with co-operating spaced through ports in both the tube passage walls and in said hollow piston rod walls for conducting power 10 fluid into each end of the motor cylinder and for conducting used power fluid out of each end of the motor cylinder, of: a valve for controlling the flow of power fluid through certain ones of said ports into each end of the motor cylinder and for 16 controlling the exhaust 01 used power fluid through certain ones of said ports out of each end of the motor cylinder; said valve being so constructed with relation to the co-operating ports in said tube passages and piston rod that, as the 20 pistons reciprocate, power fluid begins to flow from the fluid delivery passage-in said tube' into the first end of the motor cylinder ahead of the approaching piston before fluid ceases to flow from'said fluid delivery passage into the second 25 end of the motor cylinder behindthe receding piston, and exhaust motive fluid simultaneously begins to flow from the second end of the motor cylinder into the exhaust passage of said tube behindthe receding piston before the exhaust to motive fluid ceases to flow from the first end of said motor cylinderahead of the approaching piston, thus eliminating complete stoppage of motive fluid from the delivery passage and used motive fluid into the exhaust passage of-said 3 tube; and means controlled by the motor piston as it reciprocates for actuating said valve.

JOHN D. MATHEWS. 

